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WO2003071160A1 - Dispositif de train planetaire de differentiel, element et procede de mise en marche de dispositif de train planetaire de differentiel - Google Patents

Dispositif de train planetaire de differentiel, element et procede de mise en marche de dispositif de train planetaire de differentiel Download PDF

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Publication number
WO2003071160A1
WO2003071160A1 PCT/JP2003/001922 JP0301922W WO03071160A1 WO 2003071160 A1 WO2003071160 A1 WO 2003071160A1 JP 0301922 W JP0301922 W JP 0301922W WO 03071160 A1 WO03071160 A1 WO 03071160A1
Authority
WO
WIPO (PCT)
Prior art keywords
speed
planetary gear
gear
differential planetary
power source
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2003/001922
Other languages
English (en)
Japanese (ja)
Inventor
Katsumi Kimura
Toshio Miwa
Michio Takashima
Ken Usami
Kazuhiko Sugiyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ebara Corp
Original Assignee
Ebara Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ebara Corp filed Critical Ebara Corp
Priority to US10/505,218 priority Critical patent/US7211018B2/en
Priority to JP2003570034A priority patent/JP4472350B2/ja
Priority to DE60334605T priority patent/DE60334605D1/de
Priority to EP03706994A priority patent/EP1477705B8/fr
Priority to HK06100148.5A priority patent/HK1080131B/zh
Publication of WO2003071160A1 publication Critical patent/WO2003071160A1/fr
Anticipated expiration legal-status Critical
Priority to US11/712,988 priority patent/US7494438B2/en
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using externally powered electric machines
    • F16H3/725—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using externally powered electric machines with means to change ratio in the mechanical gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using externally powered electric machines

Definitions

  • the present invention relates to a differential planetary gear device, and a starting device and a starting method of the differential planetary gear device.
  • the differential planetary gear set shown in FIG. 14 includes, as basic elements of a transmission mechanism, a sun gear S g fixed to the tip of an input shaft 55 connected to a driving device 50, and a sun gear S g outside the sun gear S g in a radial direction.
  • the gear P2 is constituted by a ring gear Rg having internal teeth meshing with each other and an output shaft 65 connected to an end of the ring gear Rg.
  • a hollow shaft C a is provided as a basic element, and the input shaft 55 is inserted through the hollow shaft C a so as to be relatively rotatable, and an end face C b orthogonal to the axis center at one end of the hollow shaft C a.
  • a carrier C having first and second support shafts J 1 and J 2 erected in parallel to the center of the shaft.
  • the plurality of first planetary gears P 1 are rotatably engaged around the first support shaft J 1
  • the plurality of second planetary gears P 2 that match the first planetary gears P 1 are: It is rotatably engaged around the second support shaft J2.
  • a gear Cc is formed on the outer edge of the end face Cb of the carrier C, and this gear Cc is aligned with the braking gears 70 and 80.
  • the braking gears 70 and 80 are connected to braking devices B1 and B3 via rotating shafts 75 and 85, respectively.
  • the differential planetary gear set shown in FIG. 14 is of a double pinion type.
  • this double pinion type differential planetary gear set has many components, has a complicated structure, and has a problem that the size is increased in the radial direction. Also, it is not suitable for high-speed rotation due to mechanical imbalance in the radial direction. Furthermore, since the rotation speed is controlled by the braking devices Bl and B3, there is a problem that the control accuracy is low.
  • the rotation speed of the drive source is set near the rated rotation speed (rated rotation speed). In some cases, the speed must be increased to within ⁇ 5%. In such a case, in order to increase the rotation speed of the drive source (for example, a large-capacity constant-speed motor) to near the rated rotation speed (within ⁇ 5% of the rated rotation speed), new starting drive means is required. It becomes important.
  • the constant rotation speed of the constant-speed motor which is the drive means for starting, is lower than the above-described rated rotation speed (about the rated rotation speed ⁇ 5%). If so, it is difficult to increase the rotation speed of the driving source to near the rated rotation speed unless the speed is increased by some means. Disclosure of the invention
  • the present invention has been made in view of the above-described problems of the related art, and provides a differential planetary gear device that eliminates mechanical imbalance, has high mechanical efficiency, and is adaptable to high-speed operation.
  • Another object of the present invention is to provide a starting device and a starting method for a differential planetary gear device that reduce a load at the time of starting in a driving source (for example, a large-capacity constant-speed motor).
  • the differential planetary gear device (A, A-1, A-2) of the present invention comprises a sun gear
  • the ring gear (2) In the area between (1) and the ring gear (2), one or more in the radial direction (of the sun gear 1 and the ring gear 2) and one or more in the circumferential direction (of the sun gear 1 and the ring gear 2) It is configured as a single pinion system in which planetary gears (3) are arranged, and includes a drive source (for example, a large-capacity constant-speed motor 4 and an internal combustion engine are also possible), a speed-change power source (5), a driven member ( For example, each of the fluid machine 6 and the turbo machine) is arranged on one of the input side (I), the output side (O), and the transmission side (T),
  • the differential planetary gear apparatus of the present invention that is configured such that the c which are characterized by an electric device (small-capacity variable-speed motor), a single Since the rotation is transmitted between the sun gear and the ring gear by the planetary gear (3), the so-called “single pinion method”, it has high mechanical efficiency and is suitable for high-speed operation.
  • a small-capacity variable-speed motor is used as a power source for shifting, shifting can be performed accurately and smoothly.
  • a planetary gear (3) force S is arranged in a region between the sun gear (1) and the ring gear (2), and the drive
  • the power source for example, a large-capacity constant-speed motor 4 or an internal combustion engine
  • the power source for shifting (5) and the driven-side members (for example, fluid machinery 6, turbo machinery) are input side, output side, and speed change.
  • the power source for speed change is an electric device, and supplies the electric power (E) for rotational drive to the power source for speed change (5) when the driven member (6) decelerates. It is configured to shut off and allow the power source (5) for shifting to generate power.
  • the differential planetary gear device of the present invention configured as described above, at the time of deceleration, the generated energy is effectively used, and a device that meets the demand of the age of energy saving is realized.
  • the power source for transmission (5) can be used as a brake of the differential planetary gear device itself.
  • the electric power generated by the transmission power source (5) is supplied to the resistance means (10).
  • the resistance means for example, by using the resistance means as a brake of the differential planetary gear device itself, a new device for the purpose of decelerating or stopping the device is provided. There is no need to incorporate a braking system, nor is it necessary to apply energy to the brakes.
  • the electric power generated in (5) is regenerated (11) to the power source of the shifting power source (5).
  • the electric power generated by the transmission power source (5) is supplied to the power storage means (12).
  • differential planetary gear device (A_4, A-5) of the present invention configured as described above, when the device is in a non-acceleration state (when decelerating or maintaining a constant speed).
  • surplus energy can be recovered as regenerative power or power storage, so that energy-saving operation is always possible. While the surplus energy is being recovered as regenerative power or storage,
  • a sun gear (1), a ring gear (2), and one or more planetary gears (3) are arranged, and a driving source (for example, a large-capacity constant speed) is provided.
  • Each of the driven-side members (rotary machine 6, turbo machine) is arranged on one of the input side (I), the output side (O), and the shifting side (T).
  • the drive source (4) is configured so that the power is supplied after the rotation speed has been increased to near the rated rotation speed by a separately provided starting means.
  • the starting means includes: a speed change power source (5); a speed increasing means (13) provided on an output side of the speed change power source (5); and an output of the speed increasing means (13).
  • a rotation transmission system extending from the side to a drive source (4).
  • the rotation transmission system includes a gear (1, 3, g) of the differential planetary gear device (A-6, A-7, A-8). 2, g1) and the rotation axis (23, Cj, 21).
  • the starting device for a differential planetary gear device includes the ring gear (2).
  • the rotating shaft (output shaft 22) connected to the motor is provided with a stopping means (brake 14/40), and the stopping means (14/40) is provided with the starting means (5, 13).
  • 23, 1, 3, Cj, g2, g1, 21/3, 37, 23, 1, 3, Cj, g2, g1, 21) by the driving source (4 ) Is preferably configured to operate while the rotation speed of the ring gear is increasing to fix the ring gear (2).
  • the speed increasing means is constituted by a mechanical transmission (13).
  • a desired speed ratio can be achieved by the rotation speed input from the power source for speed change. , Work effectively.
  • the rotation speed of the drive source (4) can be quickly increased to near the rated rotation speed by the starting means.
  • the starting means includes: a power source for shifting (5); a power source for shifting.
  • the stopping means (14) applies all the torque of the power source for speed change (5) to the drive source (4). Quickly reaches near the rated rotational speed. As a result, the driven member
  • the speed increasing means of the differential planetary gear device of the present invention is configured to include an inverter motor (35) and an inverter (37).
  • the impeller may be of a type built in an impeller motor.
  • the starting of the drive source (4) is controlled by the in-park motor (35) and the inverter (37). As a result, the driving source (4) can start stably.
  • the entire device can be reduced in size and space.
  • the starting device for the differential planetary gear device according to the present invention is provided in the area between the sun gear (1) and the ring gear (2), one in the radial direction and one or two in the circumferential direction.
  • the planetary gears (3) are arranged in a single pinion system, and the power source for shifting (5) is an electric motor (for example, a variable speed electric motor 5).
  • a sun gear, a ring gear, and one or more planetary gears are arranged, and each of the driving source, the shifting power source, and the driven member is any one of an input side, an output side, and a shifting side.
  • the brake is operated to fix the ring gear
  • the inverter and the inverter motor are started to rotate the driving source to a predetermined rotation speed
  • the power is supplied to the drive source to start the drive source at the predetermined rotation speed, and the drive source is operated normally.
  • This predetermined rotation speed is the rated rotation speed of the drive source. /. Less than or equal is preferred. '
  • Electric motor for example, variable-speed electric motor 5
  • the power source (5) for shifting is used as the power source (5) for shifting.
  • the differential planetary gear group (G) has high mechanical efficiency and is suitable for high-speed operation '.
  • FIG. 1 is a block diagram showing the entire configuration of the differential planetary gear device according to the first embodiment of the present invention.
  • FIG. 2 is a block diagram showing the entire configuration of the differential planetary gear device according to the second embodiment of the present invention.
  • FIG. 3 is a block diagram showing the entire configuration of the differential planetary gear device according to the third embodiment of the present invention.
  • FIG. 4 is a block diagram showing the entire configuration of the differential planetary gear device according to the fourth embodiment of the present invention.
  • FIG. 5 is a block diagram showing the entire configuration of the differential planetary gear device according to the fifth embodiment of the present invention.
  • FIG. 6 is a block diagram showing the entire configuration of another embodiment of the present invention.
  • FIG. 7 is a block diagram showing the entire configuration of another embodiment of the present invention.
  • FIG. 8 c 9 is a proc diagram further showing the entire structure of another embodiment of the present invention is a control Furochiya one preparative showing a control related to the function change of the transmission variable speed motor of the present invention.
  • FIG. 10 is a block diagram showing the entire configuration of the differential planetary gear device according to the sixth embodiment of the present invention.
  • FIG. 11 is a block diagram showing the entire configuration of the differential planetary gear device according to the seventh embodiment of the present invention.
  • FIG. 12 shows a state at the time of starting the differential planetary gear device according to the seventh embodiment of the present invention.
  • 4 is a control flowchart showing a control method.
  • FIG. 13 is a block diagram showing the entire configuration of the differential planetary gear device according to the eighth embodiment of the present invention.
  • FIG. 14 is a block diagram showing the overall configuration of a conventional differential planetary gear device. BEST MODE FOR CARRYING OUT THE INVENTION
  • the differential planetary gear device indicated by reference numeral A is a motorized differential planetary continuously variable transmission B having an input shaft 21 and an output shaft 22 and an input side I, that is, an input shaft 2.
  • the drive unit 4 of the large-capacity, constant-speed motor connected to the end of the input shaft 1 via the input clutch 31 and the output side 0, that is, the output shaft 22 to the end of the output shaft 22 via the output clutch 32.
  • the electric differential planetary continuously variable transmission B includes a differential planetary gear group G having an input shaft and an output shaft common to the input shaft 21 and the output shaft 22 and having a drive shaft 23 for shifting. And a speed change small-capacity variable speed motor 5 connected to the speed change drive shaft 23.
  • the differential planetary gear group G includes an input gear g 1 fixed to the other end of the input shaft 21, a sun gear 1 fixed to the other end of the speed change drive shaft 23, and a carrier C, and a carrier C. It comprises a plurality of planetary gears 3 supported by C, and a ring gear 2 having one end forming the output shaft 22.
  • the carrier C has a hollow rotation axis C j and has one (input side) end.
  • An input gear g2 that is concentric with the rotation shaft Cj and matches the input gear g1 is fixed to the other end (output side) at an equal radius from the center of the rotation shaft Cj and around the circumference.
  • a plurality of planetary gear support shafts P are arranged in the same direction and parallel to the rotation axis C j.
  • the shift drive shaft 23 is rotatably inserted into the hollow portion of the rotary shaft C j of the carrier C, and the sun gear 1 fixed to the other end of the shift drive shaft 23 is connected to the plurality of planetary gears 3. It is configured to fit.
  • the plurality of planetary gears 3 are rotatably engaged around the plurality of support shafts P for the carrier C of the carrier C, and are engaged with the sun gear 1, and at the same time, the inner teeth 2 a of the ring gear 2. They are in contact.
  • the sun gear 1 and the ring gear 2 are of a so-called “single pinion type” in which rotation is transmitted by a single planetary gear 3.
  • the drive unit 4 When starting the fluid machine 6, the drive unit 4 is driven first. At the same time, the motor is started with the variable speed motor for shifting 5 set to the minimum speed. Therefore, the carrier C driven by the drive unit 4 and the sun gear 1 directly connected to the variable speed motor 5 for rotation rotate together. Then, the planetary gear 3 rotates on the carrier C at a rotation speed obtained by multiplying the relative rotation speed between the carrier C and the sun gear 1 by the gear ratio between the planetary gears 3 and the sun gear 1. Then, at a rotation speed obtained by multiplying the absolute rotation speed of the planetary gear 3 by the gear ratio of the ring gear 2 and the planetary gear 3, the rotation directly connected to the fluid machine 6 is performed. Gear 2 starts to rotate.
  • variable speed motor 5 for shifting gears is at the lowest speed, so that the fluid machine 6 is operated at the lowest speed.
  • the brake (not shown) built into the variable speed motor for speed change 5 is operated to fix the rotating shaft (sun gear 1) of the variable speed motor for speed change 5.
  • the driving device 4 is driven.
  • the sun gear 1 directly connected to the variable speed variable speed motor 5 is fixed, the rotation speed of the carrier C driven by the drive unit 4 is multiplied by the gear ratio of the planetary gear 3 and the sun gear 1.
  • the planetary gear 3 rotates on the carrier C.
  • the ring gear 2 directly connected to the fluid machine 6 starts rotating at a rotation speed obtained by multiplying the absolute rotation speed of the planetary gear 3 by the gear ratio between the ring gear 2 and the planetary gear 3.
  • the brake of the variable speed variable speed motor 5 is released, and the variable speed variable speed motor 5 starts operating at the minimum speed.
  • the planetary gear 3 rotates on the carrier C at a speed obtained by multiplying the relative rotational speed of the carrier C and the sun gear 1 by the gear ratio of the planetary gears 3 and the sun gear 1.
  • the ring gear 2 rotates at a speed obtained by multiplying the absolute rotation speed of the planetary gear 3 by the gear ratio between the ring gear 2 and the planetary gear 3. That is, the fluid machine 6 is operated at the lowest speed.
  • FIG. 1 having such a configuration, since it is configured as a single binion system, it has high mechanical efficiency and is suitable for high-speed operation.
  • the rotational speed ⁇ s of the sun gear 1 directly connected to the speed change motor 5 is changed by driving the speed change variable speed motor 5, for example, by increasing or decreasing the current. Therefore, the revolving speed co c of the planetary gear 3 that is supported by the carrier C and simultaneously engages the sun gear 1 and the ring gear 2 and revolves around the sun gear 1 is also variable.
  • the ratio (speed ratio) of the ring gear 2 corresponding to the planetary gear 3, that is, the rotation speed ⁇ of the output shaft 22 to the rotation speed ⁇ i of the input shaft 21 also becomes variable.
  • variable speed motor (variable speed motor for speed change) 5 is used as the power source for speed change, the speed change is performed accurately and smoothly.
  • the differential planetary gear set generally denoted by reference numeral A-1 has an electric differential planetary gear having an input shaft 25 (disposed on the right side in the drawing) and an output shaft 26 (disposed on the left side in the drawing).
  • a step transmission B— 1 an input side I, that is, a drive unit 4, which is a large-capacity constant-speed motor connected to an end of the input shaft 25 through an input side clutch 31, and an output side 0, that is, an output
  • the fluid machine 6 is connected to an end of the shaft 26 via an output-side clutch 32.
  • the electric differential planetary continuously variable transmission B-1 has a differential shaft having an input shaft and an output shaft common to the input shaft 25 and the output shaft 26 and having a drive shaft 23 for shifting. It is constituted by a group of star gears G-1 and a variable speed variable speed motor (small capacity variable speed motor) 5 connected to the variable speed drive shaft 23.
  • the differential planetary gear group G-1 includes: a ring gear 2-1 having one end forming the input shaft 25; an output gear g11 fixed to another end of the output shaft 26; It comprises a sun gear 11-1 fixed to the other end of the shaft 23, a carrier C-1 and a plurality of planetary gears 3_1 supported by the carrier C-11.
  • the carrier C-11 has a hollow rotating shaft C j, and an output side gear g 21, which is concentric with the rotating shaft C j and coincides with the output gear g 11, at one (output side) end.
  • a plurality of support shafts P for planetary gears are arranged at the same radial position from the center of the rotation axis C j and are arranged in the circumferential direction evenly in parallel with the rotation axis C j. ing.
  • the speed change drive shaft 23 is rotatably passed through the hollow portion of the rotation shaft C j of the carrier C-11, and the sun gear 1-1 fixed to the other end of the speed change drive shaft 23 is the same as the sun gear 1-1. It is configured to be compatible with the plurality of planetary gears 3-1.
  • the plurality of planetary gears 3-1 are rotatably engaged around the plurality of planetary gear support shafts P of the carrier C-11, and are engaged with the sun gear 1-1. It is inscribed and joined to the tooth 2a.
  • the planetary gear 3-1 is of a single pinion type, it has high mechanical efficiency and is suitable for high-speed operation.
  • variable speed motor 5 for driving is directly connected to the variable speed motor 5 for shifting by driving the variable speed motor 5 for speed change, for example.
  • Sun gear 1 — 1 rotation speed ⁇ s changes. Therefore, the revolving speed of the planetary gear 3-1, which is supported on the carrier C-1 side and simultaneously engages the sun gear 1-1 and the ring gear 2-1 and revolves around the sun gear 1-1, that is, the carrier C-1
  • the rotation speed ⁇ c can also be changed, and the speed ratio (speed change ratio) of the rotation speed ⁇ of the output shaft 26 corresponding to the carrier C-11 to the rotation speed ⁇ i of the input shaft 25 also becomes variable.
  • variable speed motor 5 is used as the power source for the speed change, and the speed is shifted by the single-binion type differential planetary gear, so that the speed change is performed accurately and smoothly.
  • the differential planetary gear device generally denoted by reference numeral A-2 is different from the first embodiment shown in FIG. 1 in that the differential planetary gear device is provided between the ring gear 2 of the output shaft 22 and the output side clutch 32.
  • a speed changing gear 7 which is a speed increasing gear or a reduction gear is added to the area.
  • FIG. 4 is a block diagram showing a fourth embodiment of the present invention.
  • the differential planetary gear G has three rotation elements of a sun gear, a planetary gear, and a ring gear, one of which is an input.
  • the other is connected to the drive unit 4 as the shaft S i, the other one is connected to the variable speed motor for shifting (small capacity variable speed motor) 5 as the transmission shaft SV, and the other is the fluid as the output shaft S o.
  • the variable speed motor for shifting (small capacity variable speed motor) 5 as the transmission shaft SV
  • the other is the fluid as the output shaft S o. Connected to machine 6.
  • FIG. 5 is a block diagram showing a fifth embodiment of the present invention, in which a driving machine 4 is connected to an input shaft S i of a differential planetary gear G via a speed increasing or reducing gear V 1, and Motor (small capacity variable speed motor) 5 also increases or decreases speed
  • the gear V 2 is connected to the speed change shaft SV of the differential planetary gear G via the gear V 2.
  • the output shaft S o of the differential planetary gear G is connected to the fluid machine 6 via a speed increasing or reducing gear V 3.
  • the present invention can be implemented in various modes.
  • the selection of the rotating element and the presence or absence of the reduction gear or reduction gear may be determined according to the degree of the speed ratio used.
  • variable speed variable speed motor small capacity variable speed It is configured so that the supply of rotational drive power to the motor 5 is cut off, the variable speed variable speed motor 5 generates power, and can also operate as a brake.
  • the variable speed variable speed motor 5 when the fluid machine 6 decelerates, the supply of the rotational drive power to the variable speed variable speed motor 5 is cut off, the variable speed variable speed motor 5 generates power, and the power obtained by the power generation is braked.
  • An example of absorption by the resistor 10 will be described.
  • the differential planetary gear device indicated by reference numeral A-3 is different from the first embodiment shown in FIG. 1 in that a speed sensor S is interposed on the output shaft 22.
  • An inverter controller 8 is provided on a power line Ld connecting the variable speed motor (small capacity variable speed motor) 5 to the external power E.
  • the inverter controller 8 and the braking resistor 10 are connected by a power line Lf, and further controlled.
  • a means (control panel) 9 is provided in which the speed sensor S, the control means 9 and the inverter controller 8 are connected via input / output signal lines Li and Lo.
  • variable speed motor 5 for shifting changes the speed of the fluid machine 6 on the output side O from a stopped state to a required speed, or In order to maintain the rotation speed of the external When electric power E is supplied, it operates so as to provide a driving force (rotation) for shifting to the sun gear 1 of the differential planetary gear group G.
  • variable speed variable speed motor 5 is also configured to function as a generator when a rotational force (driving force) is given from the speed change drive shaft 23.
  • the variable speed motor 5 when decelerating the fluid machine 6 after the fluid machine 6 reaches a certain speed (required driving force), the surplus of the driving force of the driving machine 4 and the inertia force of the fluid machine are reduced.
  • the resultant acts to give (return) the driving force to the variable speed motor 5 for shifting via the sun gear 1. That is, when the fluid machine 6 is decelerated as described above, the variable speed motor 5 generates electric power even when the external power E supplied to the variable speed motor 5 is cut off.
  • the control means 9 determines that the differential planetary gear unit A-3 is in a deceleration state based on the rotation speed of the output shaft 22 obtained from the speed sensor S. In the case of a deceleration state, the external power E to the variable speed variable speed motor 5 is shut off, and the power generated by the variable speed variable speed motor 5 flows to the braking resistor 10 side. Thus, the control signal is transmitted to the inverter controller 8. At this time, the variable speed variable speed motor 5 operates as a brake.
  • variable speed motor 5 for shifting and the power supply circuit will be described with reference to FIGS.
  • step S1 the control means 9 reads the rotation speed signal of the output shaft 22 from the speed sensor S via the input signal line L i, and in step S2, the motor-driven differential planetary continuously variable transmission B— Judge whether 3 is in the decelerating state. ⁇ Y motorized differential planetary continuously variable transmission ⁇ — If 3 is not in a decelerating state (NO in step S2), proceed to step S3 and leave the variable speed motor for shifting 5 (indicated by SM in Fig. 9) as it is. Use as motor and go to step S4.
  • step S2 If the motor-driven differential planetary continuously variable transmission B-3 is in the decelerating state (YES in step S2), the process proceeds to step S5, where the external power E is supplied to the variable speed motor 5 for shifting by the impeller controller 8. Then, the circuit is switched to send the electric power generated by the variable speed motor 5 for shifting by the inverter controller 8 to the braking resistor 10 side, and the process proceeds to the next step S6.
  • step S6 the variable speed variable speed motor 5 is made to function as a generator, the generated power is sent to the braking resistor 10, and the generated power is converted into heat by braking. Then, the process proceeds to the next Step S4.
  • step S4 the control means 8 determines whether or not to end the control. If the control is not to be ended (NO in step S4), the control returns to step SI, and if it is to be ended (YES in step S4). ), End the control.
  • FIG. 7 is different from the embodiment shown in FIGS. 6 and 9 in that the variable speed motor for shifting is used when the electric differential planetary continuously variable transmission B-3 is in the deceleration state.
  • variable speed variable speed motor ( The difference is that the electric power generated by the small-capacity variable-speed motor 5 is supplied to the storage battery 12 instead of being supplied to the braking resistor 10.
  • the inverter controller 8 and the storage batteries 12 are connected by a power line L f. The rest is substantially the same as the embodiment shown in FIGS. 6 and 9, including the control.
  • the surplus administered energy can be recovered as regenerative power or power storage, so that energy-saving operation can always be performed.
  • the variable speed motor 5 for variable speed acts as a brake member while the surplus administered energy is being recovered as regenerative power or power storage.
  • the differential planetary gear G preferably has a single-binion type configuration, but may have a double pinion type configuration.
  • the differential planetary gear set indicated by reference numeral A-6 is a motor-driven differential planetary continuously variable transmission B-4 having an input shaft 21 and an output shaft 22, and an input side I. (I.e., the input shaft 21) is connected to the end of the large-capacity constant-speed motor 4 via an input-side clutch 31; A rotating machine 6 A connected via a clutch 32.
  • a rotary machine 6A for example, a fluid machine such as a turbo machine is used.
  • the electric differential planetary continuously variable transmission B-4 has a group of differential planetary gears having an input shaft and an output shaft common to the input shaft 21 and the output shaft 22 and having a drive shaft 23 for shifting.
  • G a direct connection / speed increase switching gear 13 connected to the speed change drive shaft 23 and capable of switching between direct connection and speed increase, and a speed change small capacity connected to the direct connection Z speed increase switching gear 13 It has a variable speed motor 5 and a brake 14 interposed on the output shaft 22.
  • the differential planetary gear group G includes an input gear g 1 fixed to the other end of the input shaft 21, and an end of the speed change drive shaft 23 opposite to the direct connection / speed increasing gear 13.
  • a carrier C a plurality of planetary gears 3 supported by the carrier C, and a ring gear 2 having one end forming the output shaft 22.
  • the carrier C has a hollow rotating shaft C j, and an input side gear g 2 that is concentric with the rotating shaft C j and mates with the input gear g 1 is formed at one (input side I) end, At the other end (output side), there are provided a plurality of supporting shafts P for a planetary gear arranged at an equal radius from the center of the rotation axis C j and in the circumferential direction uniformly and in parallel with the rotation axis C j. .
  • the speed change drive shaft 23 is rotatably inserted into the hollow portion of the rotation shaft C j of the carrier C, and the sun gear 1 formed at the other end (output side O) of the speed change drive shaft 23 is It is configured to be compatible with the plurality of planetary gears 3.
  • the plurality of planetary gears 3 are rotatably engaged around the plurality of support shafts P for the carrier C of the carrier C, and are engaged with the sun gear 1, and at the same time, the inner teeth 2 a of the ring gear 2. They are in contact.
  • the so-called single pinion system is interposed between the sun gear 1 and the ring gear 2.
  • the brake 14 is configured to operate manually or automatically. When the brake 14 is operated, the output shaft 22, that is, the ring gear 2 is fixed.
  • the direct-connection / speed-up switching gear 13 is configured to selectively directly connect or increase the speed of the variable-speed motor 5 to the sun gear 1 by a switching means (not shown) and transmit the rotation.
  • the direct-coupled Z-speed-up switching gear 13 is shifted to the speed-up side almost simultaneously with the operation of the brake 14. Since the ring gear 2 is fixed by the operation of the brakes 14, the planetary gear 3 corresponding to the sun gear 1 and the ring gear 2 starts to rotate by the rotation of the sun gear (rotated by the variable speed variable motor 5). At the same time, revolve around Sun Gear 1. The revolution of the planetary gear 3 is the rotation of the carrier C.
  • the input shaft 21 having the input gear g1 that matches the input side gear g2 of the carrier C is rotated.
  • the rotation of the speed-variable variable speed motor 5 whose speed can be adjusted is further directly connected.
  • the speed is increased by 13 and transmitted to the driving machine 4, and the driving machine 4 can rapidly increase the rotation speed to near the rated rotation.
  • the load of having to rotate the rotating machine 6A at the time of starting can be reduced.
  • the operation of the brake 14 is released, and the direct connection Z-speed changeover gear 13 is switched to the direct connection side.
  • the rotating machine 6 A which is the driven side, gradually increases the rotation speed while shifting from the stopped state, and reaches the normal operation rotation speed.
  • the speed of the planetary gear group G is adjusted by adjusting the speed of the variable speed variable speed motor 5 (for example, by increasing the current value supplied to the motor) to change the rotational speed ⁇ s of the sun gear 1 directly connected to the variable speed variable speed motor 5. Changes. Therefore, The revolving speed ⁇ c of the planetary gear 3 revolving around the sun gear 1, which is rotatably supported on the gear C side and simultaneously engages with the sun gear 1 and the ring gear 2, is also variable. As a result, the ratio (speed change ratio) of the rotation speed ⁇ of the ring gear 2 corresponding to the planetary gear 3, that is, the output shaft 22 to the rotation speed ⁇ i of the input shaft 21 also becomes variable.
  • variable speed motor 5 is used as the speed change power source, and the speed is changed by the single-binion type differential planetary gear, so that the speed change is performed accurately and smoothly.
  • the differential planetary gear device indicated generally by reference numeral A-7 is different from the above-described sixth embodiment shown in FIG. 10 in that the variable speed motor 5 for speed change and the direct connection Is replaced with an inverter motor 35 and an inverter 37, a speed sensor S is interposed on the input shaft 21 and connected to the control means 9 (represented by ELU in FIG. 11) by an input signal line Li.
  • the control means 9 and the inverter 37 are connected by an output signal line Lo.
  • step S1 the control means 9 reads the rotation speed signal of the input shaft 21 from the speed sensor S via the input signal line Li, and in step S2, determines whether or not the driving machine 4 is at the start. Judge.
  • step S2 If the driving machine 4 is started (YES in step S2), the flow proceeds to step S3, the brake 14 is operated to fix the ring gear 2, and then the flow proceeds to step S4. If the driving machine 4 is not started (NO in step S2), the process proceeds to step S6.
  • step S4 the inverter 37 and the inverter motor 35 are started.
  • the inverter motor 35 rotates the sun gear 1 via the speed change drive shaft 23.
  • the rotation of sun gear 1 causes carrier C to revolve while rotating planetary gear 3 that matches sun gear 1 on its own axis.
  • the rotation (revolution) of the carrier C rotates the drive unit 4 from the input gear g2 of the carrier C via the input gear g1, that is, the input shaft 21 and the input clutch 31.
  • step S 5 that reaches the range of the soil 5% of the rated rotation speed. ° of the drive machine 4, the power to the drive motor 4 is turned on, the driving motor 4 The driving machine 4 itself is started within a range of 5% of the rated rotation speed with respect to the rated rotation speed, and the normal operation is continued as it is (step S6).
  • step S7 the control means 9 determines whether or not to end the control. If the control is not ended (NO in step S7), the process returns to step SI, and if it is ended (YES in step S7). ), End the control.
  • the control unit 9 by controlling the starting of the drive motor 4 by inverter Tamota 35 and Inbata 3 7, the drive device 4 can be stably started Obviously
  • inverter motor 35 and the inverter 37 it is possible to reduce the size and space of the entire device.
  • the differential planetary gear device generally denoted by reference numeral A-8 is different from the sixth embodiment shown in FIG. 10 described above in that a brake 14 disposed on the output shaft is provided with a speed-increasing gear and And / or a brake device with a speed change mechanism 40 having a reduction gear and a switching clutch. Switching of the "shift Z braking" is performed by manual means or automatic means (not shown).
  • a brake 14 interposed on the output shaft is connected to a speed-up gear and a Z or reduction gear,
  • the brake device 40 By providing the brake device 40 with a transmission mechanism having a switching clutch, a shift in a wider range of speed is possible as compared with the sixth embodiment shown in FIG.
  • the illustrated embodiment is merely an example, and does not limit the technical scope of the present invention.
  • the relationship between the arrangement of the driving machine 4, the variable speed motor for speed change 5, and the rotating machine 6A is not limited to the arrangement of the sixth embodiment shown in FIG.
  • each of the drive unit 4, the variable speed motor 5 for speed change, and the rotary machine 6A can be appropriately arranged on the three shafts of the differential planetary gear unit. Can be configured. Which of the six types of arrangement examples should be used may be determined according to various usage conditions (speed ratio used, etc.).
  • control as shown in the seventh embodiment of FIGS. 11 and 12 can be applied in the sixth embodiment and the eighth embodiment.
  • the start of the drive source is controlled by the inverter motor and the inverter, so that the drive source can start stably.
  • the present invention can be suitably used for a differential planetary gear device and a starting device and a starting method of the differential planetary gear device.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
  • Stopping Of Electric Motors (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Control Of Ac Motors In General (AREA)

Abstract

L'invention concerne un dispositif de train planétaire de différentiel, caractérisé par une conception de type à pignon unique comprenant un train planétaire (3) monté radialement et un ou deux trains planétaires (3) ou plus montés sur la circonférence, dans une zone située entre une roue solaire (1) et une couronne (2). Selon l'invention, une source d'entraînement (4), une source d'entraînement de changement de vitesse (5) et un élément entraîné (6) se trouvent sur des côtés comprenant un côté entrée (I), un côté sortie (O) et un côté changement de vitesse (T), la source d'entraînement de changement de vitesse (5) étant une machine dynamoélectrique.
PCT/JP2003/001922 2002-02-21 2003-02-21 Dispositif de train planetaire de differentiel, element et procede de mise en marche de dispositif de train planetaire de differentiel Ceased WO2003071160A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US10/505,218 US7211018B2 (en) 2002-02-21 2003-02-21 Differential planetary gear device, and differential planetary gear device starting device and starting method
JP2003570034A JP4472350B2 (ja) 2002-02-21 2003-02-21 差動遊星歯車装置の始動装置
DE60334605T DE60334605D1 (de) 2002-02-21 2003-02-21 Startvorrichtung umfassend eine Planetendifferentialgetriebevorrichtung und Startverfahren für eine Planetendifferentialgetriebevorrichtung
EP03706994A EP1477705B8 (fr) 2002-02-21 2003-02-21 Dispositif de mise en marche comprenant un dispositif de train planétaire différentiel et procédé de mise en marche de dispositif de train planétaire différentiel
HK06100148.5A HK1080131B (zh) 2002-02-21 2003-02-21 差动行星齿轮装置、及其起动装置和起动方法
US11/712,988 US7494438B2 (en) 2002-02-21 2007-03-02 Starting apparatus for differential planetary gear apparatus

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2002044215 2002-02-21
JP2002-044215 2002-02-21
JP2002044224 2002-02-21
JP2002-044224 2002-02-21

Related Child Applications (1)

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US11/712,988 Division US7494438B2 (en) 2002-02-21 2007-03-02 Starting apparatus for differential planetary gear apparatus

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WO2003071160A1 true WO2003071160A1 (fr) 2003-08-28

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PCT/JP2003/001922 Ceased WO2003071160A1 (fr) 2002-02-21 2003-02-21 Dispositif de train planetaire de differentiel, element et procede de mise en marche de dispositif de train planetaire de differentiel

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US (2) US7211018B2 (fr)
EP (1) EP1477705B8 (fr)
JP (1) JP4472350B2 (fr)
CN (1) CN100425869C (fr)
DE (1) DE60334605D1 (fr)
HK (1) HK1080131B (fr)
WO (1) WO2003071160A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010242811A (ja) * 2009-04-02 2010-10-28 Kuchida Gearing:Kk 変速装置
WO2016009668A1 (fr) * 2014-07-18 2016-01-21 三菱重工コンプレッサ株式会社 Système de moteur électrique variable et dispositif associé alimenté électriquement
JP2019148293A (ja) * 2018-02-27 2019-09-05 三菱重工コンプレッサ株式会社 可変速増速機及び可変速増速機の制御方法
US10465774B2 (en) 2015-09-04 2019-11-05 Mitsubishi Heavy Industries Compressor Corporation Starting method for variable speed accelerator and starting control device for variable speed accelerator
US10473193B2 (en) 2015-09-04 2019-11-12 Mitsubishi Heavy Industries Compressor Corporation Control method for variable speed electric motor system and control device for variable speed electric motor system
US10544862B2 (en) 2015-09-04 2020-01-28 Mitsubishi Heavy Industries Compressor Corporation Starting method for variable speed accelerator and starting control device for variable speed accelerator
US10605339B2 (en) 2016-02-26 2020-03-31 Mitsubishi Heavy Industries Compressor Corporation Variable speed accelerator and control method for variable speed accelerator
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US11025180B2 (en) 2016-06-15 2021-06-01 Mitsubishi Heavy Industries Compressor Corporation Variable speed accelerator

Families Citing this family (47)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8082088B2 (en) * 2005-09-20 2011-12-20 Volvo Construction Equipment Ab Method for controlling rotation speed
GB2431441A (en) * 2005-10-22 2007-04-25 Jcb Transmissions Infinitely variable transmission with speed changing electric motor
US7791235B2 (en) * 2006-12-22 2010-09-07 General Electric Company Variable magnetic coupling of rotating machinery
CN100425870C (zh) * 2007-03-27 2008-10-15 邹政耀 行星齿轮式无级变速传动系统
US20090133953A1 (en) * 2007-11-28 2009-05-28 Delphi Technologies, Inc. Power steering system having a variable-ratio drive mechanism for a vehicle
DE102009019485A1 (de) 2008-12-09 2010-06-10 Isatec Gmbh Antriebsstrang mit einem ersten Elektromotor und einem Planetengetriebe sowie Windenergieanlagen, Gasturbinen und Wasserturbinen und Fahrzeuge, die diesen Antriebsstrang aufweisen
US7828686B2 (en) * 2009-03-19 2010-11-09 General Electric Company Yaw assembly for a rotatable system and method of assembling the same
US8330291B2 (en) * 2009-10-02 2012-12-11 General Electric Company Power generation apparatus
US8827853B2 (en) * 2010-07-08 2014-09-09 Parker-Hannifin Corporation Hydraulic power split engine with enhanced torque assist
US8763709B2 (en) * 2010-10-07 2014-07-01 Schlumberger Technology Corporation Electrically driven coiled tubing injector assembly
CN102072285A (zh) * 2010-12-31 2011-05-25 杨新胜 一种高精度高效率的减速器
CN102062175A (zh) * 2010-12-31 2011-05-18 杨新胜 一种高精度高效率的减速器
US10760654B2 (en) * 2012-05-08 2020-09-01 Robert C. Kennedy Variable speed drive system
AT514281A3 (de) 2013-05-17 2015-10-15 Gerald Dipl Ing Hehenberger Verfahren zum Betreiben eines Triebstranges und Triebstrang
AT514589B1 (de) 2013-05-17 2015-02-15 Gerald Dipl Ing Hehenberger Verfahren zum Betreiben eines Triebstranges und Triebstrang
AT514396B1 (de) * 2013-05-17 2015-11-15 Set Sustainable Energy Technologies Gmbh Verfahren und Vorrichtung zum Anfahren eines Triebstranges
DE102014201324A1 (de) * 2014-01-24 2015-07-30 Siemens Aktiengesellschaft Drehzahlveränderliche Maschinen-Getriebe-Einheit
CA2931101C (fr) * 2014-02-20 2018-05-29 Halliburton Energy Services, Inc. Mecanisme de commande de vitesse/position en boucle fermee
AT14302U1 (de) * 2014-03-17 2015-08-15 Gerald Dipl Ing Hehenberger Verfahren zum Betreiben eines Triebstranges und Triebstrang
AT516180B1 (de) * 2014-08-19 2016-03-15 Gerald Dipl Ing Hehenberger Verfahren zum Anfahren eines Triebstranges und Antrieb hierfür
CN107112854B (zh) * 2014-10-14 2020-01-17 安德烈亚斯·巴斯特克 用于驱动变速工作设备的装置和方法
DE102014115191B4 (de) * 2014-10-14 2019-04-25 Andreas Basteck Vorrichtung und Verfahren zum Antrieb von drehzahlvariablen Arbeitsmaschinen
DE102014225738A1 (de) * 2014-12-12 2016-06-16 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Antriebsstrangs
EP3051177B1 (fr) * 2014-12-15 2021-03-17 Rolls-Royce plc Dispositif d'entraînement à vitesse variable
US10760497B2 (en) 2015-02-23 2020-09-01 Mitsubishi Heavy Industries Compressor Corporation Gas turbine starting device and gas turbine system
DE102015002585B4 (de) 2015-03-02 2018-08-16 Andreas Basteck Vorrichtung und Verfahren zum Antrieb von drehzahlvariablen Arbeitsmaschinen mit Drehzahluntersetzung
CN105443684A (zh) * 2015-12-22 2016-03-30 中国兵器工业集团第二○二研究所 行星轮传动无极增速机构
WO2017145350A1 (fr) 2016-02-26 2017-08-31 三菱重工コンプレッサ株式会社 Dispositif d'augmentation de vitesse à vitesse variable
WO2017195321A1 (fr) 2016-05-12 2017-11-16 三菱重工コンプレッサ株式会社 Mécanisme d'accélération à vitesse variable
JP6566285B2 (ja) * 2016-06-15 2019-08-28 三菱重工コンプレッサ株式会社 可変速増速機、及び可変速増速機の制御方法
WO2017216888A1 (fr) 2016-06-15 2017-12-21 三菱重工コンプレッサ株式会社 Accélérateur à vitesse variable et procédé de démarrage d'accélérateur à vitesse variable
DE112016006959B4 (de) 2016-07-20 2022-03-31 Mitsubishi Heavy Industries Compressor Corporation Getriebe mit variabler drehzahl
EP3491273B1 (fr) * 2016-07-26 2020-04-29 Voith Patent GmbH Dispositif d'entraînement muni d'un engrenage de superposition
WO2018029804A1 (fr) 2016-08-10 2018-02-15 三菱重工コンプレッサ株式会社 Multiplicateur de vitesse variable
US10865855B2 (en) 2016-08-29 2020-12-15 Mitsubishi Heavy Industries Compressor Corporation Variable-speed speed-up gear
CN106545637A (zh) * 2016-10-31 2017-03-29 广西柳工机械股份有限公司 动力分配调节系统及装载机动力系统
FR3062424B1 (fr) * 2017-01-30 2021-02-12 Safran Aircraft Engines Systeme d'entrainement d'une pompe a carburant d'une turbomachine
DE102018101082B4 (de) * 2018-01-18 2021-03-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Antriebsanordnung zum Antrieb von wenigstens drei Fluidpumpen
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JP7136671B2 (ja) 2018-11-26 2022-09-13 三菱重工コンプレッサ株式会社 可変速増速機の製造方法及びシャフト用治具
DE102019102881B4 (de) * 2019-02-06 2022-06-02 Renk Gmbh Verfahren und Steuergerät zum Betreiben eines Antriebstrangs mit Haupt- und Zusatzantrieb und Überlagerungsgetriebe
IT202000020593A1 (it) 2020-08-28 2022-02-28 Nuovo Pignone Tecnologie Srl Disposizione di azionamento per una attrezzatura ad azionamento meccanico e metodo di funzionamento della stessa
IT202000020596A1 (it) 2020-08-28 2022-02-28 Nuovo Pignone Tecnologie Srl Metodo per far funzionare un sistema a treno per un’attrezzatura ad azionamento meccanico
CN112283306A (zh) * 2020-11-16 2021-01-29 中国船舶重工集团公司第七0三研究所 恒速传动装置
FI131663B1 (en) * 2022-05-13 2025-09-01 Neptunus Trans Oy Gearbox
US12384616B1 (en) * 2025-01-08 2025-08-12 Permco, Inc. Digital power take-off

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5869146U (ja) * 1981-11-02 1983-05-11 住友重機械工業株式会社 回転駆動装置
US4514991A (en) * 1983-10-17 1985-05-07 Carrier Corporation Variable speed drive motor system with inverter control
JPH06249305A (ja) * 1993-02-28 1994-09-06 Hino Motors Ltd 車輛のエネルギ回生装置
US5396214A (en) * 1993-10-21 1995-03-07 General Electric Company Dynamic braking grid resistor configuration for reducing EMI in an electric traction motor vehicle
US5433282A (en) * 1992-05-19 1995-07-18 Kabushikikaisha Equos Research Hybrid vehicle powered by an internal combustion engine and an electric motor
JPH1182649A (ja) * 1997-09-16 1999-03-26 Honda Motor Co Ltd 無段変速トランスミッション
US5947854A (en) * 1997-05-08 1999-09-07 Worksmart Energy Enterprises, Inc. Combined variable-speed drive and speed reducer for pumps and fans

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2436582A (en) * 1943-08-28 1948-02-24 Lear Inc Variable-speed control system
US2436936A (en) * 1944-05-22 1948-03-02 Herbert E Page Variable-speed drive
US3503281A (en) * 1966-03-08 1970-03-31 Voith Getriebe Kg Power transmitting plant with controllable fluid coupling
JPS5869146A (ja) 1981-10-20 1983-04-25 Nec Corp 多重変換装置
FR2609499B1 (fr) 1987-01-09 1990-11-23 Lajarrige Pierre Groupe motopropulseur a variation continue de vitesse
US4973295A (en) * 1989-03-31 1990-11-27 Gabrielle Reng-Yi Wu Lee Stepless variable ratio transmission
US5019755A (en) * 1989-04-11 1991-05-28 Walker David E Electric motor drive system
US5508574A (en) * 1994-11-23 1996-04-16 Vlock; Alexander Vehicle transmission system with variable speed drive
JP2794272B2 (ja) * 1995-02-28 1998-09-03 株式会社エクォス・リサーチ ハイブリッド車両及びハイブリッド車両の制御方法
JP3712910B2 (ja) 2000-03-23 2005-11-02 トヨタ自動車株式会社 車両の変速機制御装置
US6648785B2 (en) * 2001-12-05 2003-11-18 New Venture Gear, Inc. Transfer case for hybrid vehicle

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5869146U (ja) * 1981-11-02 1983-05-11 住友重機械工業株式会社 回転駆動装置
US4514991A (en) * 1983-10-17 1985-05-07 Carrier Corporation Variable speed drive motor system with inverter control
US5433282A (en) * 1992-05-19 1995-07-18 Kabushikikaisha Equos Research Hybrid vehicle powered by an internal combustion engine and an electric motor
JPH06249305A (ja) * 1993-02-28 1994-09-06 Hino Motors Ltd 車輛のエネルギ回生装置
US5396214A (en) * 1993-10-21 1995-03-07 General Electric Company Dynamic braking grid resistor configuration for reducing EMI in an electric traction motor vehicle
US5947854A (en) * 1997-05-08 1999-09-07 Worksmart Energy Enterprises, Inc. Combined variable-speed drive and speed reducer for pumps and fans
JPH1182649A (ja) * 1997-09-16 1999-03-26 Honda Motor Co Ltd 無段変速トランスミッション

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1477705A4 *

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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US10454394B2 (en) 2014-07-18 2019-10-22 Mitsubishi Heavy Industries Compressor Corporation Rotational driving force imparting device and electric motor device for the same
WO2016009564A1 (fr) * 2014-07-18 2016-01-21 三菱重工コンプレッサ株式会社 Dispositif de communication de force d'entraînement en rotation et son dispositif de moteur électrique
WO2016010146A1 (fr) * 2014-07-18 2016-01-21 三菱重工コンプレッサ株式会社 Système de moteur électrique variable et dispositif à alimentation électrique
JPWO2016009564A1 (ja) * 2014-07-18 2017-04-27 三菱重工コンプレッサ株式会社 回転駆動力付与装置、及びその電動装置
JPWO2016010146A1 (ja) * 2014-07-18 2017-04-27 三菱重工コンプレッサ株式会社 可変電動機システム、及び電動装置
JPWO2016009668A1 (ja) * 2014-07-18 2017-05-25 三菱重工コンプレッサ株式会社 可変電動機システム、及びその電動装置
RU2639319C1 (ru) * 2014-07-18 2017-12-21 Мицубиси Хэви Индастриз Компрессор Корпорейшн Система регулируемого электрического двигателя и устройство с электрическим приводом, входящее в состав этой системы
US10177692B2 (en) 2014-07-18 2019-01-08 Mitsubishi Heavy Industries Compressor Corporation Variable electric motor system and electrically powered device
WO2016009668A1 (fr) * 2014-07-18 2016-01-21 三菱重工コンプレッサ株式会社 Système de moteur électrique variable et dispositif associé alimenté électriquement
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US10677324B2 (en) 2016-02-26 2020-06-09 Mitsubishi Heavy Industries Compressor Corporation Variable speed accelerator
US10837526B2 (en) 2016-05-20 2020-11-17 Mitsubishi Heavy Industries Compressor Corporation Variable-speed speed-up mechanism
US11025180B2 (en) 2016-06-15 2021-06-01 Mitsubishi Heavy Industries Compressor Corporation Variable speed accelerator
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JP7014638B2 (ja) 2018-02-27 2022-02-01 三菱重工コンプレッサ株式会社 可変速増速機及び可変速増速機の制御方法

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US20070155570A1 (en) 2007-07-05
JPWO2003071160A1 (ja) 2005-06-16
JP4472350B2 (ja) 2010-06-02
EP1477705B8 (fr) 2011-01-26
EP1477705A1 (fr) 2004-11-17
US7494438B2 (en) 2009-02-24
HK1080131A1 (zh) 2006-04-21
US20050113201A1 (en) 2005-05-26
EP1477705A4 (fr) 2006-05-03
EP1477705B1 (fr) 2010-10-20
CN1639485A (zh) 2005-07-13
CN100425869C (zh) 2008-10-15
US7211018B2 (en) 2007-05-01
HK1080131B (zh) 2009-03-06
DE60334605D1 (de) 2010-12-02

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